Hermetic refrigeration compressor



Feb. 3, 1953 J. TOUBORG HEIRMETIC REFRIGERATION COMPRESSOR Filed Sept.27, 1948 4 Sheets-Sheet 1 Fig.2. 1 i ii F 4}? 5. v: r T i l u i l fattorney Feb. 3, 1953 J. TOUBORG 2,627,170

HERMETIC REFRIGERATION COMPRESSOR Filed Sept. 27, 1948 4 Sheets-Sheet 24 51 V 6 L u r 11" 67' Imnentor 71 7 Jensfozzozg,

24 7113 89 as WQW Clttrneg Feb. 3, 1953 OUBORG 2,627,170

HERMETIC REFRIGERATION COMPRESSOR Filed Sept. 27, 1948 4 SheetsSheet 5Jens T0 Feb. 3, 1953 J. TOUBORG 2,627,170

HERMETIC REFRIGERATION COMPRESSOR Filed Sept. 27, 1948 4 sheets sheet 411 111 91,1 1 I 28 a, 11 l 94.

325 g 101 03 1 F 9 8 2113: 1 85 F1981] 7 z 1 87 1 Q 121 131' M1 10 11191% 127 A 1 1 I12 T V I 12 Pip-9 Zmnemor Jens fouwrg,

CI orneg Patented Feb. 3, 1953 HERMETIC REFRIGERATION COMPRESSOR JensTouborg, Tecumseh, Mich., assignor to Tresco, Inc., Tecumseh, Mich., acorporation of Michigan Application September 2'7, 1948, Serial No.51,348

Claims. 1

This invention relates to a hermetic or sealed compressor, and it hasparticular reference to an improved compressor applicable torefrigeration systems. The compressor herein disclosed has subjectmatter in common with that described in my copending application SerialNo. 774,323, filed September 16, 1947, and now Patent No. 2,540,062,January 30, 1951, and accordingly this application may be deemed to be acontinuation inpart.

One purpose of the invention is to provide a hermetic compressor,incorporating a fractional horsepower motor, which is extremely compactand of relatively small dimensions for its compressive capacity. Whenassembled in or with refrigeration cabinets, a greater percentage of thecabinet volume may therefore be given over to the cooling compartment.

Another object of the invention is to provide an improved internalresilient mounting for the compressor cylinder and motor, whereintransversely disposed springs are employed to mount the movable parts inpredetermined and spaced relation to the casing walls. Other objects ofthe invention are to provide an improved lubricant circulating pump; toprovide built-in mufller chambers further to minimize the development ofnoise; to provide for the recirculation of compressed and cooledrefrigerant through the lubricant, thereby to absorb heat from thecompressor and increase its operating efficiency; and generally toprovide improvements conducive to economics in manufacture anddurability and high efllciency in operation.

The invention will be readily understood from the following descriptionof a typical embodiment, illustrated in the accompanying drawings,wherein:

Fig. l is a side elevation of the compressor as assembled with aflue-type or static condenser on a domestic refrigerator cabinet.

Fig. 2 is a rear elevation of the compressor and condenser assemblyshown in Fig. 1.

Fig. 3 is a vertical section through the compressor, with certain partsshown in elevation.

Fig. 4 is a bottom plan, the compressor casing being shown in section.

Fig. 5 is an enlarged view, partly in section and partly in elevation,as viewed from the left of Fig. 3.

Fig. 6 is a section on the line 6-6 of Fig. 5.

Figs. 7 and 7A are companion views, on an enlarged scale, illustratingthe relations between piston, crank, and lubricant pump during thecompression stroke of the piston. They are taken on irregular se t onines through the same Parts shown in Fig. 3, looking up from the bottom.

Figs. 8 and 8A are also companion views, taken the same as Figs. 7 and7A, showing the relations between the same parts during the suctionstroke of the piston; and

Fig. 9 is a perspective of the crankshaft crosshead. 1

' In Figs. 1 and 2, there is illustrated a hermetic compressor generallydesignated by the reference numeral 20, as it may appear when assembledin a complete refrigeration system for a domestic food storage cabinet.The working partsof the compressor, hereinafter described, are enclosedin a sealed casing 2| having generally the form of a relatively shortcylinder. A mounting bracket 22, welded or otherwise secured to theperiphery of the casing, serves to suspend the compressor from a rail orbracket 23 mounted transversely on the rear wall of a domesticrefrigerator cabinet 24, and in such manner that the axis of the casingis disposed horizontally. The rail 23 also forms a part of a verticallypositioned, flue type, condenser 25, extending over the rear wall of thecabinet, and above the compressor 20. The refrigerator cabinet isinvariably set up against a wall 26 of the kitchen or other room whenplaced in service, and the space between the walls thereby forms a flueor stack, through which air will flow by induced draft to remove theheat of compression. from the refrigerant flowing in the system. This isone way in which the parts may be assembled, but it should be understoodthat other assembly plans may be utilized insofar as the compressoritself is concerned.

The condenser 25 is formed from a length of tubing 21, bent back andforth a few times in serpentine fashion, and a second longer length oftubing 28,"also bent back and forth. The straight portions or runs ofthe tubes are equipped with longitudinally extending fins 29, hereinshown as channels having their webs soldered or otherwise connected toopposite sides of the tubes. and their flanges 3| extending inwardlytoward each other. Brackets, such as the bracket 23 and comparablebrackets 32, are secured to the tube runs at the ends of the fins 29,and adjacent the return bends 33, to integrate the structure and give itdesirable rigidity. It will be seen that the facing channel shaped finsprovide independent air flues, apart from the stack made by bringing thecabinet 24 close to the wall 26. ,A further description of the condenseritself will be; found in my copending' application, Serial No: 51,347,filed September 27, 1948, now abandoned.

The purpose inproviding two lengths of tubing 2i and 28, instead of onecontinuous length, is to eifect recirculation of cooled refrigerant intothe compressor crankcase and oil bath. The inlet end of the tube 21 isconnected to a discharge line 36 directly connected to the compressorexhaust, While the other end of the tube 2'! is connected to a duct 35which also enters the casing 2i, and is there connected to a coolingcoil submerged in the oil bath, as will hereinafter be explained indetail. The compressed refrigerant then fiOWs again out of the casing 2|through a line 36- which is connected to the inlet end of the tube 28,through which it flows, with concomitant cooling by the induced airdraft, to the condenser outlet 31, located at the opposite end of thetube 28. The refrigerant then flows through a strainer 38 and supplyline 39 to an evaporator ell located in the cabinet 24, and is returnedto the compressor 26 through a suction line :12 which discharges intothe casing 2 I. Inasmuch as the control of the cycle of operation isconventional, it is deemed unnecessary to illustrate the elementsemployed for this purpose, or to describe in detail the electricaloverload and starting relays, contained in a box '43 secured'to theexterior of the casing 2!, from which extends an electrical service cordat for connection to a source of current.

The construction of the compressor 29 is more fully illustrated in theremaining views. As shown in Figs. 3, 4, and 5, the. casing 2| is formedof two sheet metal shells i and 52, one of which is somewhat deeper thanthe other, and each of which is formed with an annular flange 53 toprovide abutting rims which can be weldedto each other to seal thecasing. Within the casing is a hermetic compressor unit, comprising anelectric motor 55, a casting55, and a refrigerant pump 55, all of whichare connected together and are resiliently mounted in spaced relationtothe casing walls. The casting 55 is generally cannular in form, and itis provided at diametrically opposed points with outstanding lugs 57,each of which is transversely bored to accommodate mounting means, asWill presently be. described. The casting is centrally formed withqanupstanding bearing boss 58 which is axially bored to receive avertically disposed main shaftiil, whose ends project both above andbelow the/boss 58.

The upper end of the shaft 59 receivesabored and counterbored quill 6|whose internal shoulderseats on-the upper end of the boss '58 to providea thrust and supporting bearing. The quill may be afiixed to the shaftby a press fit, set screw, or like means, and its external surface ispressedinto a rotor 62 for the motor 54. The motor stator 63 is seatedinan annular shoulder 6.4, formed in the upper .rim .ofthe casting 5.5,and it is retained ingpositionby bolts 65 (Fig. 4), extending upwardlythrough suitably located apertures. The motor lead wires 66 extendthrough an aperture 6'! in the body of the casting to insulatedterminals ,63 which pass through the wall of the she1l'5l forconnectionto the relays contained in the box .43.

The casting 55 and the parts connected thereto are internallymounted inthe casing 2| by a resilient suspensionv cooperating with the castinglugs 51. The casing sections'Bl and 52 are each provided with spaced padportions H and 12, re spectively, located substantially radiallyequidistant'from the longitudinal axis of the'cylindri'cal dimension ofthe casing, and in an axial plane parallel thereto. Opposed pads maytherefore be brought into axial alignment when'the casing shells aresuperimposed. As best shown in Figs. 4 and 5, each pad is provided, onits inner surface, with abutments or sockets 13 which may convenientlybe welded thereto. The ends of transversely disposed spring supportingand retainer rods 14 extend into and are supported by the alignedsockets, and these rods pass through coarsely tapped openings 15 in thelugs 57. Each rod is surrounded by a coiled spring 16, and these springsalso pass through the opening 15, and abut the ends of the sockets 13.

Inasmuch as the springs 16 are helical, and are herein shown also asbeing cylindrical, they may be screwed into the apertures 75 to projecton each side thereof the correct distance, in order to center or locatethe compressor assembly with respect to the casing walls. While thesprings are thus in contact with the lugs, they do not touch the rods 73, except at the end turns, which are bent on a progressively decreasingradius, as will be apparent from Fig. 6. The end turns are also bent toapproximately circular, rather than helical form, to engage as much aspossible the end surfaces of the abutments 13. Each end of the rods 14is formed with a small key H, which can enter any one of a number ofkeyways it formed in the sockets 13, thereby retaining the rod fromrotation. These keys also provide rotational stops for the ends of thesprings, which abut the keys on one side thereof, while the end turnsclosely engage the periphery of the rod, passing tangentially to theopposite sides of the keys as they merge into the spiral convolutions ofgreater diameter. Both rods and springs are therefore restrained fromrotation after assembly, and the springs may be accurately adjustedbetween the ends of the sockets.

The spring mounting and suspension just described Will fullyandadequately support the casting assembly in the casing in the desiredspaced relation to the walls thereof. Rotative forces tending to turnthe entire assembly around the axis of the shaft 59 are absorbed by thesprings acting under compression, or axially, while forces acting in'avertical direction are counteracted by the rigidity of the springs 15considered as beams. Among such vertical forces is the Weight of thecasting assembly, which tends to bend the springs 16 so that theycontact the rods '54 at the lugs 57. In some instances, the total weightof the casting assembly is such that, in order to give the springs itenough resistance against fiexure to prevent their bottoming on the rodsi l, it is necessary to sacrifice some of the desired softness along theaxial direction. The result of such sacrifice is an inability of thesprings it, when acting in compression, to absorb or damp out a much ofthe vibratory forces imposed thereon as is desired, resulting in thetransmission of a greater amount of the vibrations to the casin walls,and with it some noise.

In order to counteract this possibility, and to maintain the noise ofoperation at the lowest possible level, and at the same time retain theover-all casing dimensions to a minimum, a portion of the total weightof the casting assembly is borne by coiled tension springs '53, whoseends are hooked respectively in pierced brackets 8i, connected to anddepending from the inner peripheral wall of the shell 5i, and ears 32 onthe upper portions of thelugs 5?. The springs 1'9 may be made :tosupport such portion of the total weight as is desired,andproportionately the springs it may bemade softer, and thus moreeifectively absorb the forces which would otherwise be transmitted tothe casing. The matter thus becomes one simply of selecting two sets ofsprings having rates compatible with the total weight of the castingassembly, the horsepower of the motor, and the duty expected from thecompressor, so that vibration and noise may be reduced to a minimum. Inso selecting the springs, it is apparent that, by giving to themdifferent natural rates or vibration frequencies, they may act togetherto suppress any adventitious vibratory influence which might be inharmony with one or the other. Forced or sustained vibrations arethereby damped by lack of resonance.

In the course of assembly, the motor 54, casting 55, and refrigerantpump 56 are initially assembled as a unit, and the rods I4 and springsI6 are also assembled with each other and through the lugs 51. Thecasing shell 5I is then laid on its side, as shown in Fig. 4, and theends of the rods 14 are placed in the sockets I3 and are locked fromrotation therein by the keys 11, which enter whatever keyway adjustmentpurposes may dictate. The springs 19 are then connected, and, aftereffecting such other connections as are indicated, that is, the wires66, etc., the shell section 52 is positioned, with the upper ends of therods entering the companion sockets 13 in such shell. When the flanges53 abut, the springs 16 will be placed under some compression, tendingto expand their convolutions, and securely and resiliently mounting theworking parts within the casing.

The refrigerant pump unit 56 comprises a cyl inder block 85, having acylinder 86 bored therein, whose head end is covered by a valve plate 81and a cylinder head 88 bolted thereto. The cylinder block assembly issecured to the under side of the casting 55 by bolts 89. A piston 9| isreciprocably mounted in the cylinder 86 by means of an offset or crankportion 92 formed on the lower end of the shaft 59, and below a crankarm 93 which carries a counterweight 94. The crank 92 rotatably fitsinto a vertical bore 95 of a crcsshead 96 (see also Figs. 7 to 9), whichis carried for transverse reciprocatory movement in a yoke 91,integrally connected to the crank end of the piston 9I. The drivingconnection will thus be recognized as being of the Scotch yoke type.

Refrigerant vapors returning to the compressor 29 through the suctionline 42 enter the casing 2| at the upper part, circulate around themotor 54 to absorb some of its heat, and then pass into a suction tubeI9I extending from one side of the head end of the cylinder block 85 tothe upper portion of the casing. It will be noted that the upper endof'the'tube [9| is creased axially along a diameter, so that theopposite walls contact, and thus. in eifectform a double-barreledsection I92, through which the returning refrigerant is inducted. It hasbeen discovered that by dividing the total crosssectional area of thetube I9I into a number of smaller areas, a slight hissing noise, causedby pulsation of the inducted refrigerant vapors, is thereby eliminated.I

As best shown in Figs. 7 and 8, the cylinder block 85 is formed withlaterally extending portions I03 and I94, each of which is internallycored to provide mufller chambers I95 and I96 respectively forbothincoming and discharging refrigerant. The lower end of the suction tubeI9! is positioned in a duct III'I communicating with the chamber I95,and a second duct I98 leads from the chamber to a cavity I99 in. thecylinder head 88, which in turn encompasses inlet ports H9 in the valveplate 81, covered by a suction valve III. Refrigerant is accordinglyinducted into the cylinder 86 on the suction stroke of the piston 9| asindicated by the arrows in Fig. 8. On the compression stroke,illustrated in Fig. 7, the refrigerant is forced through ports H2 andpast a discharge valve H3 into a spaced cavity H4 in the head 88, andthence through a duct H5 communicating with the discharge mufflerchamber I96. The refrigerant then flows through a duct H6 into adischarge tube II'I, coiled in a bath of oil contained in the casing 2I,and which terminates in the discharge line 34 leading to the condenser,as previously ex plained.

The provision of built-in muffler chambers in the block 85, for both theinlet and discharge sides of the cylinder, greatly reduces the tendencyto develop noise, and also simplifies the construction and assembly. Asthe discharge tube HI tends to vibrate from the pulsating fiow ofcompressed refrigerant, its formation into a coil, and

disposition in the oil bath, also asuppresses another potential cause ofsome noise.

It Was heretofore noted that the condenser 25 is divided into twosections, and that the refri erant, after some cooling in the tube 21,is returned to the casing 2| through a line 35. This line is connectedto one end of a length of tubing I I8, advantageously formed as asubstantially flat spiral and disposed in the oil bath beneath thedischarge coil I I1, as will readily be apparent from Figs. 3, 4., and5. The other extremity of the tube H8 is directly connected to the line36. leading to the other portion 28 of the condenser 25. Forconvenience, both ends of the tube H8 may be to the same side of thecasing 2I for connection to the ducts 3'5 and 36. This arrangementprovides an effective and simple method of extracting heat from thelubricant and compressor, and maintaining operating temperatures withindesirable limits. Heat is transferred to the oil from the hotrefrigerant passing through the discharge coil HI, and is extracted fromthe, oil by the relatively cool refrigerant returned from the condenserto flow through the coil I I8.

The cooling of the oil bath is very useful when the compressor 29 isassembled into a high side unit with a static condenser, that is, asystem wherein an auxiliary condenser air fan and motor are omitted.Under heavy working loads, the over-all heat generation may overtax thecapacity of the natural draft of cooling air, thus leading to excessivetemperatures for motor and compressed refrigerant, With concurrentreduction in efficiency and risk of motor failure; It has. beendiscovered that, by recirculating compressed, but relatively coolrefrigerantthrough the oil bath, a compressor temperature reduction mayreadily be effected which maintains themachine within desiredtemperature limits, and thus maintains a higher capacity. This method ofheat extraction eliminates the necessity of a-stand-by auxiliarycondenser fan and attendant controls, or a separate oil cooling radiatorand circulating pump outside of the casing 2i While the section 21 ofthe condenser 25 is herein shown as being utilized .for the pre-coolingof the compressed refrigerant,

it should be understood that-a separate precooler may be used. Itis;also apparentthat the pre-cooler section may be =made as large or assmall as operating conditions may warrant, and will depend upon thedesireddegre of oil cooling.

a through the axis of the piston 9!.

is enclosed by a lubricant pump cylinder casing i128, formed from anumber of laminated plates which are welded together, and to the underside The normal oil bath levelis approximately at the bottom of thepiston '9'I,'so that it can carry a lubricating film into the cylinder99 as the piston reciprocates. Oil is supplied to the bearings for themotor 54 by a force feed pump, generally designated by the referencenumeral I'2I in Fig. 3, which operates iii-unison with the reciprocationof the piston 9|. The pump effiuent is supplied to the bearings throughan axial duct I22 in the shaft 59, which extends from the bottom orcrank end 92 to a point just below the upper extremity, where it mergesinto a radial bore I23. A similar bore, not shown, located on the mainshaft section just above the crank arm 93, supplies a portion of thelubricant in the duct I22 to a spiral groove I24 on the periphery of theshaft, to furnish-oil to the main and thrust bearings. The upper boreI23 communicates with an'aligned radial opening in the quill 6i, and theportion of oil discharging therethrough is splattered over the rotor 62to aid in cooling. Thus, in addition to the cooling of the motoreffected by the returning refrigerant, further cooling is obtained bythe lubricant. As just noted, the oil is cooled by the pro-cooled compressed refrigerant. The lubricant discharged through both quill 6| andspiral groove I2 3 drains to the bottom of the casting 55 for returnthrough the aperture 61.

The operation of the pump I26, and its synchronization with the shaft 59and piston 9!, will be more readily understood by reference to Figs. '1to 9. The closed but hollow piston 9! is welded to the cylindricalandopen-ended yoke 91, with their axes intersecting at right angles in ahorizontal plane. The upper portion of the yoke cylinder is formed withan elongated slot 526 to receive the crank 92 and to accommodate itsaxial component of motion, while the lower portion of the yoke 91 isformed with an arcuate slot or port I21, which is disposed on thecentral diameter and is therefore intersected by a vertical plane Theslot 421 of the yoke 91,'and are bored to provide a pump cylinder I29whose head end communicates with the port I21. This formation of theyoke and pump cylinder assembly provides a sturdy but light weightconstruction, and also simplifies problems of fabrication.

The piston I3I for the cylinder I29 consists of a fixed horizontal pinscrewed into a tapped opening in the head end of the block 85, whoseaxis is located in the vertical planepassing through the axis of thepiston9I. This pin has a diameter somewhat less than the diameter of thecylinder I29, and, upon the suctionstroke, admission of lubricantto thecylinder'l29 is effected by leakage under suction pressure through theclearance gap. Dischargeof lubricant, of course, is throughthe port 621in communication with the head end of the cylinder I29, the dash poteffect precluding significant reverse flow through the clearance gapduring the compression stroke. The length of the pin I-3I is such thatits inner end is guided in the cylinder I29 at all times.

The cylindrical crosshead 96, which is closed at its ends, is mediallyintersected by the bore 95 Which provides a bearing for the crank 92.The length of the crank is such as to terminate-at the innermost chordtaken through the arcs of intersection of the bore and'crossheadperiphery. Ac-

cordingly, there'is provided a small spherical segmental cavity or'wellI32 (Fig. 3) below the end of the shaft 59 and the inner wall of theyoke 91, with which the shaft duct I22 is in constant communication. Thecrosshead 96 is also formed adjacent one end with a circumferentiallymilled slot I33, intersecting the bore 95, and extending arcuately forsomething less than ninety degrees. This slot is so located as to bealigned with the port E21upon the compression stroke, and displacedtherefrom durin the suction stroke of the compressor.

In Fig. 7, the piston 9| is shown at substantially its mid positionduring the compression stroke, the direction of rotation being as shownby the arrow on the counterweight 94. At this point, it will be seenthat the crosshead slot I 33 overlaps or registers with the port. I21 inthe yoke 91, thus placing the lower end of the shaft duct I22 in fluidcommunication with the cylinder I29 through the well I32. Inasmuch asthe motion of the yoke 91 is then toward the left, as viewed in Figs.7'and 7A, lubricant will be discharged to the duct I22 by thecompressiveeifect of the motion of the cylinder I 29 over the piston I3I.

At this particular instant, the motion of the crosshead is upward, asseen in Fig. 7, while the axis of the crank 92 is at a position ofapproximate intersection with the axis of the yoke 91. Accordingly,during the ensuing ninety degrees of rotation, the piston 9| andcylinder I29 will continue to move toward the left, to complete thecompression strokes of both the refrigerant and the lubricant pumps.During such movement, however, the motion of the crosshead 96 isdownward, and the slot I33 is so located, and of such width, that itwill pass completely over the duct I 21, to cut off dischargetherethrough as the end of the compression stroke is reached. At thismoment, the crosshead is located substantially centrally in the yoke 91.

After the axis of the crank 92 has swept through the axis of the pistonIN, the reciprocatory motion of the piston and yoke is reversed. Thecylinder I29 is retracted from its piston I3 I, while the'piston 9|begins its motion to the right. During the first ninety degrees ofrotative m0vement corresponding to these linear movements,

the crosshead 96 continues to move downwardly,

to attain the position shown in Fig. 8. The next ninety degrees ofrotative motion from the position of Fig. 8 completes the suctionstrokes for both pumps, and reverses the motion of the crosshead toreturn it to its central location. Further rotation institutes thecompression strokes, the slot I33 again realigning with the port I21 toopen the discharge from the cylinder I29, and the parts returning to thepositions of Fig. 7 to complete the cycle.

It will be seen that the lubricant feed pump I2I is of extremely simpleconstruction, and it has but one moving part. The discharge valvecontrol is effected through the crosshead and yoke assembly, and againno additional movable parts are required in addition to the essentialcomponents of the drive. It has been found that this lubricant pump willdeliver ample quantities of oil to the motor for both lubricating andcooling purposes, and there is no significant leakage 'around the pistonI 3| or the crosshead 99 on the compression stroke. 'Inasmuch'as thepiston I31 is not in direct contact with the cylinder I29, there is nolikelihood of wear to interfere with the efficiency of operation.

.It is believed that the functioning of the complete compressor has beenmade apparent as the detailed description has developed. The problem ofproviding high compressive capacity into a small unit is solved in partby locating the motor shaft diametrically of the casing 2|, and inproviding a resilient suspension disposed at least in part axially ofthe casing and transversely of the motor assembly. This springsuspension also provides a metallic path to conduct heat to the casingwalls. Other heat conducting media include the oil sprayed over themotor, the incoming refrigerant vapors, and the cooling coil H8cooperating with the condenser 25.

It has been a very diflicult matter to build hermetic compressors on alow cost, high production, basis which would operate with aninsignificant amount of noise. In the instant machine, the submergenceof discharge and cooling coils, and utilization of built-in mufiiers,contribute to the solution of the noise problem, as also does theresilient suspension. The simplification of the structural details, andtheir coordination with each other, cooperate to maintain residual noiseat a non-disturbing low level, and withal permit quantity manufacture ata low unit cost.

Obviously, many of the advantages of the invention may be obtained whenutilizing only some of its improved features, and it will be alsoapparent that various modifications and changes may be made withoutdeparture from its principles. Accordingly, it is intended that theinvention should not be restricted to the precise parts and completecombination as herein shown and described, but that it be accorded ascope commensurate with that expressed in the following claims.

I claim:

1. A hermetic refrigeration compressor comprising a sealed casing, acasting within the easing having a motor and compressor operativelyconnected thereto, spring means to support the casting in spacedrelation to the casing walls, inlet and discharge ports for thecompressor, an imperforate discharge line connected to the dischargeport and extending through the wall of the casing, a suction lineopening in the wall of the casing at a high point therein and incommunication with the interior of the casing, a suction conduit in thecasing having one end connected to the inlet port of the compressor andits opposite end disposed at a high point in the casing in spacedrelation to the suction line opening, whereby refrigerant vapor to becompressed may circulate in the casing before entering the suctionconduit, said suction conduit adjacent its open end being divided into anumber'of openings each smaller than the total cross sectional area ofthe suction conduit to muille noise generated by the pulsation of vaporsin said conduit.

2. A compressor comprising a supporting casting formed with a shaftbearing, a rotatable drive shaft mounted in the bearing, said shafthaving a crank extending from one side of the bearing, a compressorcylinder block connected to the casting, a reciprocable piston mountedin the cylinder block, a Scotch yoke connection between the crank andpiston, a lubricating pump cylinder formed in the yoke element of saidScotch yoke, a fixed pump piston mounted on the cylinder block andextending into the pump cylinder, an oil duct extending axially of theshaft and through the crank, said oil duct communicating with thebearing, a discharge port in the yoke element in fluid communicationwith the pump cylinder and adapted to be covered by the crossheadelement of the Scotch yoke, and a slot formed in the crosshead elementand intersecting the crank bore therein and adapted periodically to bealigned with and displaced from the discharge port as the cross headelement reciprocates in the yoke element.

3. A compressor comprisinga supporting casting formed with a shaftbearing, a rotatable drive shaft mounted in the bearing, said shafthaving a crank extending from one side of the bearing, a compressorcylinder block secured to the casting, a reciprocable piston mounted inthe cylinder block, said piston having a yoke on the crankcase endthereof. said yoke having an axial slot and a radial slot in theperiphery thereof, an oil pump cylinder secured to the periphery of theyoke and having a head end in fluid communication with said radial slot,said radial slot forming a discharge port for the pump cylinder, acrosshead reciprocably mounted in the yoke and having a boretherethrough, said crank being mounted in the bore and extending throughthe axial slot whereby the crank may rotate in the bore and reciprocatethe crosshead in the yoke and the compressor piston in the compressorcylinder block, a fixed pump piston on the crankcase end of the cylinderblock extending into the pump cylinder, an axial oil duct formed in theshaft and extending from the crank end thereof to said bearing, saidduct thereby being in communication with the crosshead bore, and aperipheral slot formed in the crosshead and in-- tersecting the bore atone side thereof, said crosshead being so positioned in the yoke thatthe peripheral slot therein registers with the radial slot in the yokewhen the yoke pump cylinder advances over the pump piston, and isdisplaced therefrom to close the radial slot when the pump cylinder isretracted.

4. A compressor comprising a supporting casting formed with a shaftbearing, a drive shaft rotatably mounted in the bearing and having acrank on one end extending therebeyoncl, a compressor cylinder blocksecured to the casting and formed with a cylinder, a piston reciprocablymounted in said cylinder, a fixed pump piston secured to the crankcaseend of the cylinder block, a driving connection between the compressorpiston and the crank, a pump cylinder operatively carried by saiddriving connection for reciprocable movement over the pump piston as thecompressor piston is reciprocated, said pump piston being of'lessdiameter than the pump cylinder to provide a clearance gap therebetween,said pump cylinder and piston being adapted to be submerged in an oilbath whereby oil may flow into the piston through said gap, a dischargeport for the pump cylinder at the head end thereof, an axial oil ductthrough the crank and shaft communicating with the shaft bearing, andvalve means controlled by the rotation of the crank to place said pumpcylinder discharge port in communication with the shaft duct uponcompressive movement of the compressor piston and to close said pumpdischarge port upon reverse movement.

5. A refrigeration high side comprising a hermetic compressor includinga casing having an interconnected motor and compressor sealed therein, apool of lubricant in the casing, pump means for circulating thelubricant over the motor to extract heat therefrom and transfer saidheat to the pool, a suction inlet in the casing adjacent the motor toadmit relatively cool refrigerant vapors into contact with the motor toextract heat therefrom, a closed discharge line extending from thecompressor through the casing wall, an imperforate cooling coil in thecasing andthe pool of lubricant therein, said coil having inlet andoutlet ends projecting through the casing, a condenser connected to thedischarge line, exteriorly of the casing to efiect cooling of thecompressed refrigerant, said condenser having its discharge endconnected to the inlet of the cooling coil, whereby cooled refrigerantmay extract heat from, the pool of lubricant and thereby the hermeticcompressor, and a second condenser having its inlet connected to theoutlet of the coil, whereby the heat absorbed by compressed refrigerantcirculating through the coil may be dissipated.

JENS TOUBORG.

REFERENCES CITED The following references are of record in the file ofthis patent:

Number 12 UNITED STATES PATENTS- Name Date I Paulsen Aug. 31, 1920Bourne Nov. 22, 1932 Philipp Feb. 14, 1933 Bixler Jan. 21, 1936 BixlerSept. 20, 1938 Steenstrup- Sept. 20, 1938 Buchanan Dec. 13, 1938 ToubergFeb. 7, ,1939 Philipp Feb. '7, 1939 Simons Mar, 5, 1940 Philipp Jan. 14,1941, I-Iigham ,June 16, 1,942 Philipp Oct. 27, 1942, Smith Mar. 2, 1943Schlumbohn Dec. 14, 1943 Touborg Nov. 28, 194 1 Hintze Mar. 12, 1946Heitchue Mar. 1, 1949

